Lubricating apparatus



March 2,- 1965 J. E. OLSEN ETAL LUBRICATING APPARATUS 8 Sheets-Sheet l Filed April 6, 1962 INV TORS LEONARD J UTTON ILL/AM M. PETERSON BY ){MM 1'- M T s E. 0 SEN JAME L TLUBRICANT na u ATTORNEYS March 2, 1965 J. E. OLSEN ETAL 3,171,510

LUBRICATING APPARATUS Filed April 6, 1962 8 Sheets-Sheet 2 LUBRICANT FIG. 6'

IN TORS JAMES E. OLSEN LEONARD X B'urTo/v 5 WILLIAM M. PETERSON ATTOQNEYS March 2, 1965 J. E. OLSEN ETAL 3,171,510

LUBRICATING APPARATUS Filed April 6, 1962 s Sheets-Sheet s FIG. 7

y grow JAMES E. OLSEN, LEONAQD urro- 6 WILLIAM M. PETERSON ATTORNEYS March 2, 1965 J. E. OLSEN ETAL 3,171,510

LUBRICATING APPARATUS Fi led April 6, 1962 8 Sheets-Sheet 4 RT we [80 (w 406 4 LUBRICANT I68 F IG. 9

n ygwoRs JAMES E. OLSEN, LEONARD UTTON WILLIAM M. PETERSON .MM %M/6km ATTORNE Y5 March 2, 1965 J. E. OLSEN 'ETAL 3,171,510

LUBRICATING APPARATUS Filed April 6. 1962 8 Sheets-Sheet 5 INV TORS J ME E. OLSEN LEONARD Zfiurrow A 5 5 M/BILlAA/l M. PETERSON ATTORNEYS March 2, 1965 J. E. OLSEN ETAL LUBRICATING APPARATUS 8 Sheets-Sheet 6 Filed April 6, 1962 III IIIL J E 0 SEN LEONAQD HI B Q'I N AMES z.

a MlL/AM M PETEQSON ATTORNEYS March 2, 1965 J. E. OLSEN ETAL LUBRICATINGAPPARATUS 8 Sheets-Sheet 7 Filed April 6, 1962 8 Sheets-Sheet 8 Filed April 6, 1962 QNs WOQN

4 1 v TORS JAMES E. OLSEN, LEONARD I). Ban-0N & BIXIFLIAM M. PETERSON ATTORNEYS United States Patent 3,171,510 LUBRICATENG APPARATUS James E. Oisen and Leonard J. Button, Royal flak, and

William M. Peterson, Clawson, Mich, assignors to Olsen Manufacturing Company, Royal Oak, Mich, a

corporation of Michigan Filed Apr. 6, 1962, Ser. No. 185,641 Claims. (Cl. 18415) This invention relates to lubricating apparatus and more particularly to apparatus for automatically lubricating conveyors or the like.

The present invention is concerned with the problem of supplying lubricant from a central, fixed source to the bearings of moving apparatus while the same is in motion, such as to the trolley wheels of endless chain conveyors or to the wheels of rail mounted trucks such as those found in steel mills. The bearings for such wheels require lubrication and are often subjected to severe conditions, such as when the conveyor or truck passes through ovens or washing apparatus. Hence it is desirable to lubricate each hearing by an automatic device, either continuously at a frequency of say once for each cycle of the conveyor or truck system, or at a frequency which may be programed automatically or manually depending on operating requirements.

It is an object of the present invention to provide improved lubricating apparatus which automatically applies a measured quantity of lubricant under high pressure to a lubricant injection point of a conveyor as the injection point reaches a lubricating station along its path of travel.

Another object is to provide a lubricator which is capable of injecting lubricant charges successively into the lubricant fittings of an endless conveyor and which automatically accommodates for variations in the spacing, elevation and/or lateral position of the fittings relative to one another.

A further object is to provide apparatus for automatically lubricating conveyor wheels or the like having a multiplicity of lubricant fittings for each wheel.

Yet another object is to provide apparatus for automatically and simultaneously lubricating two or more wheels of a conveyor of the type wherein alternate wheel shafts each have a plurality of lubricant fittings arranged in patterns reversed or otherwise alternating from one another.

A still further object of the present invention is to provide an automatic lubricating apparatus of the above character having a rapid cycle of operation in a simplified construction which provides reliable operation and economy in manufacturing and operating costs.

Other features and advantages of the lubricating apparatus of the invention will become apparent in the following description and drawings in which:

FIG. 1 is a plan view of one embodiment of the lubricating apparatus of the present invention in the retracted position thereof.

FIG. 2 is a plan view of a portion of the lubricating apparatus of PEG. 1 in the injection position thereof.

FIG. 3 is a fragmentary sectional view taken on the line 3-3 of FIG. 1.

FIG. 4 is a fragmentary sectional view taken on the line 44 of FIG. 1.

FIG. 5 is a fragmentary side elevational view of the lubricating apparatus of FIG. 1.

FIG. 6 is a fragmentary sectional view taken on the line 6-6 of FIG. 5.

FIG. 7 is a sectional view taken on the line 7-7 of FIG. 2.

FIG. 8 is a rear elevational view of the lubricating apparatus of FIG. 1.

3,171,510 Ratented Mar. 2, 1965 FIG. 9 is a diagrammatic showing of the pneumatic and lubricant supply systems of the lubricating apparatus of FIGS. 1-8.

FIG. 10 is a side elevational view taken in section on the line 1tl-1tl of FIG. 14 illustrating a modified form of lubricating apparatus also in accordance with the present invention.

FIG. 11 is a fragmentary plan view of a portion of the apparatus of FIG. 10 illustrating a multiple nozzle head thereof in its extended, pick-up position.

FIG. 12 is a sectional view on the line 1212 of FIG. 14 with portions shown partially in elevation.

FIG. 13 is an end elevational view of the multiple nozzle head of FIG. 12.

FIG. 14 is a rear elevational view of the modified lubricating apparatus arranged in a dual unit system for simultaneous lubrication of alternate conveyor wheels having reversed fitting patterns.

FIG. 15 is a diagrammatic showing of the pneumatic and lubricant supply systems of the modified lubricating apparatus in a dual unit arrangement.

Referring to FIG. 1, an improved lubricating apparatus of the present invention is shown in conjunction with a flanged conveyor wheel 20 running on a rail 22. The hub of each wheel 20 has a conventional lubricant fitting 24, illustrated herein as the extended Zerk type fittings by means of which grease can be directed to the wheel bearings. The lubricating apparatus is arranged on a C-frame 26 mounted on a suitable support 28 positioned alongside the conveyor rail 22 (FIG. 8).

The lubricating head (FIGS. 1, 7 and 8) is mounted on a base 39 bolted to frame 26 and adapted to support said head which includes an upright yoke 32 for swivel movement about a vertical axis. Base 30 is provided with small and large diameter annular seats 34 and 36 (FIG. 7) which respectively support the outer races of ball bearings 38 and it), the inner races of which in turn support a stepped bearing shaft 42 of yoke 32. A flanged ring 44 on base 30, a felt sealing ring 46 and a dust cover 48 mounted on a flange 51 of yoke 32 together provide a seal against dirt and dust entering the ball bearings.

A main air cylinder 52 is supported within the horizontal bore 54 of yoke 32 by a ring 60 which encircles cylinder 52 generally at the center of gravity thereof and Which has a pair of oppositely extending co-axial pivot pins 56 (FIGS. 2 and 8) journalled in a pair of bearings 58 of the yoke. Cylinder 52 is thus supported in the manner of a trunnion for pivotal movement in a vertical plane about the horizontal axis of pins 56 and for swivel movement in a horizontal plane about the vertical axis of yoke bearing shaft 42.

A piston 62 within cylinder 52 is adapted to reciprocate between an end cover plate 64 and a stop ring 66. Plate 64 is provided with a fittting 68 for admitting air into cylinder 52 to thereby drive piston 62 towards stop 66, and a coil spring 70 is provided Within cylinder 52 for biasing piston 62. back to the retracted position thereof adjacent plate 64. A hollow piston rod 72 is connected at one end to piston 62 and extends therefrom through a bearing ring 74 and out the front end of cylinder 62.

The term lubricating head as used herein generally refers to the aforementioned yoke 32, main air cylinder 52, piston 62 and piston rod 72, or equivalent sub-assemblies, and the component parts associated therewith.

A lubricating nozzle 76 is threaded into a flanged end plug 78 which in turn is inserted in and welded to the outer end of piston rod 72. Nozzle 76 has a conically recessed outer end face 80 which is several times the diameter of the extended Zerk type lubricant fitting 24. Recess 80 serves to cam the nozzle into registry with fitting 24 in the event the latter is misaligned. It is to be unierstood that the, outer. end face nozzle 76 may be rerersed in form, i.e., pointed, so as to function in the same nanner to orient the nozzle, when the lubricant fittings zre of the conventional flush type and hence likewise re- Iersed in form from extended fittingsr A reduced cenl'ral passage 82 in nozzle 76 communicates with a counter- Jore 84 therein which in turn communicates with a pas- ;age 86 in end plug 78 leading to an external lubricant aupply line fitting 88.

The main air cylinder 52 is yieldably maintained in a aorizontal, centered position by a compression coil spring (FIGS. 1 andS) which is held between a pair of paraltel mounting brackets 92 and 94 secured respectively to 7 yoke 32 and supporting ring 60. The opposite sides of :enteri'ng spring each extend through a vertical. slot provided in each bracket 92, 94. The slots are slightly narrower in transverse dimension than the diameter .of the spring so as to hold the same in place. The opposite ends of the slots in brackets 92, 94 act to compress spring 90 whenever cylinder 52 is pivoted about the axis of pins 56 out of its normal horizontal. position, either up or down, as might be caused by the camming engagement of nozzle 76 with a misaligned lubricant fitting 24.

Upon disengagement of nozzle 76 from the lubricantfitting, spring 90 expands and returns cylinder 52 to its horizontal, centered position.

Referring again to FIG. 7, base 30 has a cavity 96 for receiving a helical torsion spring 98 which is wound around yoke bearing shaft 42. The bottom convolution of spring 98 is bent into a straight portion 100 which is received in a bore 102 of base 30, and the uppermost convolution is secured to yoke shaft 42. Torsion spring 98 is adapted to rotate yoke 32 counterclockwise so as to yieldably hold cylinder 52 in the angled ready position of FIG. 1 wherein the axis of the cylinder is approximately 10 degrees in advance of the perpendicular injection position of FIG. 2. When piston rod 72 is extended so as to carry nozzle 76 to the angle pick-up position illustrated in broken lines in FIG. 1, the nozzle 76 engages lubricant fitting 24 and then the movement of conveyor wheel 20 swivels cylinder 52 about the rotational axis of yoke hearing shaft 42, thereby tensioning torsion spring 98; Upon retraction of piston rod 72 and release of nozzle 76', torsion spring 98 unwinds and then swivels cylinder 52 in the reverse direction to return it to the angled position of FIG. 1.

A cam ring 106 (FIGS. 7 and 9) is secured by capscrew 104 to shaft 42 so as to rotate therewith, the outer periphery of cam 106 being provided with a recess 108 and a camming surface 109 which actuates a detent plunger 110 mounted for axial movement in a bearing 112 which in turn is fitted in a bore 114 of base 30. V Plunger 11 0 is biased towards vcam 166 by a compression coil spring 116 which bottoms against a bracket 118 affixed to base 30 so as toclose. off bore114. A push rod 120 is connected atone end to plunger 110 and extends through a bearing in bracket 118 and threadably receives a pusher 122 on theouter end thereof. Pusher 122 is adjustably secured in position by a lock nut 124 and serves to ac tuate a plunger 125 of an air valve 126 mounted on bracket 118 when cam 106 is rotated by swivel movement of cylinder 52 to its right angle injection position (FIGS. 2 and 9).

When the frequency of lubrication is to be continuous, an actuator mechanism is provided for sensing'the approach of a conveyor wheel 20 to the lubricating station. As best shown in FIGS. 1 and 8, the upper horizontal plate 128 of frame 26 supports a pair of journal brackets 130 which rotatably support a camshaft 132. The outer end 'of shaft 132 extends to a point above the path of travel of wheel 20 (FIG. 1) and threadably receives a retainer sleeve 134 and a lock nut 136 on'the end'thereof.

Suitable meansis provided for causing rotation of shaft 132'and correlating such rotation with the position of a wheel 20 relative to the lubricating station. Byway 4 of illustration there is shown an actuator rod 138 adjust ably held by retainer 13450 as to extend vertically downward into the path of travel of wheel 20. Rod 138 is maintained in this position by a counterweight 140 connected to the opposite end of shaft 132 which exerts a clockwise torque on the shaft. as viewed in FIG. 3 so as to'maintain a pin 142 extending from shaft 132 against a stop 144 (FIG; 3). I

A cam 146 (FIGS. 1 and 4) is secured to shaft 132 adjacent an air valve 148, cam 146 having arise portion 150 which depresses the plunger of valve .148 when rod 138 is pivoted from the vertical position to the first inclined position P (indicated respectivelyin solid and broken lines inFIG. 3) as a result of wheel 20 moving to the pick-up position indicated in broken lines in FIG. 1. Actuation of valve 148 connects-an air inlet line 152 with an air outlet line-154 leading from valve 148 to cylinder 52 to thereby drive piston 72 from the retracted to the pick-up position wherein nozzle 76' engages lubricant fitting 24.

It is to be noted that actuator rod 138 and cam 146 are adjusted to cause extension of piston 72 when lubricant fitting 24 is in alignment with the axis of cylinder 52. However, should lubricant fitting 24 be misaligned either vertically or' horizontally, the conical face 80 of nozzle '76 will cam the nozzle into registry with the lubricant fitting, the centering spring 90 and torsion spring 93' permitting pivotal and swivel movement respectively of cyli-nder 52 to compensate forthe'lub'ricant fitting misalignment. Even nore irnp'ortant should the lubricant,

fitting 24 be laterally misaligned from its normal position i due to side sway of the conveyor, the telescoping movement of nozzle 76 will cause it to engage fitting 24 even 1 though the fitting is closer to or farther from 'the lubri- I eating head than is normally the case;

The above lubricating head mechanism is pneumatically actuated'by compressed air fed from a suitable source of supply via air line 156 (FIG. 5) to a conventional air filter 158, through a conventional air line lubricator 160, and then in parallel-to a pressure regula-' tor 162'and air line 164. Air line 152 connects pressure regulator 162 with airvalve 148, the pressure regulator 162- allowing suitable adjustment of the engagement pressure of nozzle76; A conventional speed control valve 166 (FIG. 1) couples air line 154 to inlet fitting 68 of cylinder '52 and permits regulated air flow to cylinder 52 and unrestricted exhaust flow from cylinder 52. It is' preferred to adjust pressure regulator 162 and speed control 166 for quick action of piston 72' without causing Branch air line 164 supplies compressed air to air valve 126 (FIG. 1) which controls the air supply fed via an air line 168 to an air cylinder 170 of a lubricant metering valve 172.

The lubricant supply system for feeding grease or other suitable lubricating fluid ,to nozzle 76 comprises a suitable source of lubricating fluid (not shown) which is preferably pressurized to supply lubricant at a pressure within the range of 1000 to 3000 psi. via a high pressure lubricant line 174 to the metering valve 172 (FIGS. 1 and 5).

Referring to FIG. 6 the lubricant metering valve 172 comprises a metering cylinder 176 having an axial bore 178 communicating at one end with lubricant inlet line 174. A shuttle shaft 180 is mounted for reciprocation in bore 178 and comprises a pisto1r182 having a large diameter shaft 184 extending axially from one face thereof and a smaller diameter shaft 186 extending axially from the opposite face thereof. Bearings 188 and 190 slidably support shafts 184, 186 respectively. The chamber 187 which is formed in bore 178 between piston 182 and bearing 18.8 communicate via a passage 192 with a passage 194 provided in a valve cylinder 196 mounted adjacent metering cylinder 176. Passage 194 opens into an axial bore 198 of valve cylinder 1%. A valve spool 200 is slidably mounted in bore 198 and is connected at one end to a piston 202 reciprocably mounted in air cylinder 170. A coil spring 204 urges piston 202 to retracted position shown in FIG. 6, and in this position a reduced shank 206 of valve spool 260 permits communication, via bore 198, between passage 194 and a passage 208 spaced axially therefrom. Passage 208 communicates with a passage 210 in metering cylinder 176, passage 216 opening into the outer end of the chamber 211 formed between piston 182 and sleeve bearing 190. Due to the differential areas of piston 182, shuttle 181) is forced to the right as viewed in FIG. 6 when lubricant pressure equalizes on both sides of piston 182. Movement of shuttle 180 to the right is limited by an adjustment screw 212 threaded into the end of an adjustment cap 214 secured to one end of meter cylinder 176. With this arrangement the amount of lubricant flowing into chamber 211 may be varied, for example, between and 1.5 cubic inches.

When air is admitted under pressure from line 168 to cylinder 171), piston 202 is forced to the left, thereby moving valve spool 200 to the position indicated in broken lines in FIG. 6 wherein passage 194 is closed by valve spool 20!) and the reduced shank 266 of the valve spool permits communication via bore 198 between passage 208 and a high pressure lubricant outlet line 216. The pressurized lubricant admitted to chamber 187 via line 174 forces piston 182 to the left, thereby forcing the contents of chamber 211, via line 216 and fitting 88 of piston 72, to the lubricating nozzle 76 (FIG. 1).

The operation of the above described lubricating apparatus may be summarized by reference to the diagrammatic showing of FIG. 9. An approaching wheel 20 strikes actuator rod 138, causing it to pivot towards the uppermost inclined position I indicated in broken lines in FIG. 3. Cam 146 rotates with actuator rod 138 and actuates air valve 148 when wheel 21) reaches pickup position P indicated in broken lines in FIG. 1, thereby connecting air line 152 with air line 154 so that compressed air is admitted to cylinder 52 to drive piston 72 from the retracted position to the pick-up position (FIG. 1). Engagement of nozzle 76 with lubricant fitting 24 causes cylinder 52 to be swiveled by conveyor movement to the injection position (FIG. 2) wherein the axis of cylinder 52 is perpendicular to the path of travel of wheel 20. When cylinder 52 reaches the injection position, cam 106 depresses the plunger of air valve 126, thereby connecting air line 164 with air line 168 so that compressed air is admitted to air cylinder 170 of metering valve 172. This drives valve spool 200 outward so that passage 210 is connected with lubricant outlet line 216 leading to nozzle 76. The lubricant under high pressure in inlet line 174 acts on shuttle piston 182, thereby forcing a metered charge of lubricant into lubricant fitting 24 under high pressure.

Further travel of wheel 20 allows actuator rod 138 to ride back down from position P to the vertical position where it is maintained by counterweight 140. This return pivotal movement of rod 138 causes cam 146 to release the plunger of air valve 148, thereby closing off line 152 and opening line 154 to an exhaust port of valve 148. Upon release of air pressure on piston 72, the spring 70 retracts piston 72 to thereby disengage nozzle 76 from lubricant fitting 24. Upon disengagement of nozzle 76, torsion spring 98 swivels cylinder 52 rapidly back to the retracted, ready position indicated in solid lines in FIG. 1. As the head returns to this position plunger 110 of air valve 126 enters recess 168 of cam 106, shutting off air line 164 and connecting air line 168 to an exhaust port of valve 126 so that air pressure is relieved in cylinder 170 of metering valve 172. Spring 2114 thereupon retracts spool 2110 so that the lubricant metering valve is recharged with lubricant from supply line 174. The above cycle is repeated as each lubricating fitting 24 moves into position adjacent the lubricating apparatus.

Referring to FIGS. 10 and 11, there is shown a modified lubricating apparatus in accordance with the present invention for lubricating conveyor wheels 238 of the type having a plurality of lubricant fittings arranged on the wheel axle 232 in a predetermined pattern, such as a triangular pattern wherein three fittings 234, 236 and 238 are spaced 120 degrees apart, around the hub 240 of the axle 232 (FIG. 14).

A plurality of such fittings are customarily employed where it is desired to simultaneously lubricate several different bearing points along the axle.

In order to simultaneously inject lubricant into the three fittings 234, 236 and 238, a triple nozzle head 242 having three lubricating nozzles 244, 246 and 248 mounted thereon in a pattern corresponding to that of lubricant fittings 234, 236 and 238 is provided on the end of a hollow piston rod 250. Piston rod 250 is formed as a sleeve integrally connected to piston 62 in cylinder 52.

Referring to FIGS. 12 and 13, each nozzle 244, 246 and 248 has a reduced stem 252 slidably received in a bore 254 extending parallel to the axis of a cylindrical nozzle retainer 256. An axially elongated slot 258 extends radially from each bore 254 to the outer periphery of retainer 256 for receiving a high pressure lubricant supply hose 260 which has a threaded connection with stem 252. An internal nozzle passage 262 connects line 260 with the conical face of the nozzles. The oversize slot 258 permits axial travel of the nozzle in bore 254 between an extended position illustrated in FIG. 12 and a retracted position as illustrated by the position of nozzle 248 in FIG. 11. Each nozzle is biased to the extended position by a coil spring 264 mounted in the corresponding bore 254.

Nozzle retainer 256 has a seal cap 266 bolted to its rear face. The rear face of retainer 256 is formed with a shoulder 268 and an axially extending shaft 270. Shaft 270 is journalled in a bushing 271 retained in a nut 274 which is threaded into the outer end of the hollow piston rod 250. Thrust bearings 272 are provided at the opposite ends of nut 274. The inner end of shaft 270 is pinned to rotate with the enlarged end 276 of a coaxial shaft 280 which is free to rotate within piston rod 250. Piston rod 250 is slotted at 284 to receive a pin 286 threadably mounted in cylinder ring 60 to prevent rotation while permitting reciprocation of piston rod 250 relative to cylinder 52. Shaft 280 is urged to the right as viewed in FIG. 12 by a coil spring 288 acting against a shoulder of a cam shaft 290 slidably mounted within piston rod 250. Cam shaft 290 is keyed against rotation by a pin 292 received in an axially extending slot 294 in piston rod 251). The outer end of cam shaft 290 is notched to provide a V shaped camming face 296, and a pair of cam follower rollers 298 are journalled on a pin 301) extending transversely through shaft 280 so as to ride against the notched cam face 296. This engagement permits rotation of nozzle retainer 256 relative to piston 25% from the centered position illustrated in FIG. 12, such rotation causing cam rollers 298 to drive cam shaft 296 axially to the left against the pressure of spring 288. When there is no torque acting on the nozzle head 242, the cam shaft 290 bearing axially against rollers 298 causes them to roll into the V-bottoms of the notched camming face 296, thereby rotating the nozzle head back to the centered position thereof.

The operation of the above described multiple nozzle lubricating head is similar to the previously described single nozzle lubricating head in that the approach of conveyor wheel 230 actuates rod 138 to actuate piston 62 and extend piston rod 250 from the retracted position indicated in broken lines in FIG. 10 to the angled pick-up position illustrated in FIG. 11. However, in the multiple nozzle embodiment each of the lubricating nozzles 244, 246, 248 can individually retract against the pressure of their associated springs 264, thereby allowing rod 250 to 1 continue outward movement until all of the nozzles have engaged the three lubricant fittings 234, 236, 238. Hence,

substantially simultaneous fitting engagement is assured even though these fittings are all located in a plane parallel to the path of travel of Wheel 230 and hence at an angle to the axis of the lubricating head in the pick-up position.

mounting ofthe lubricating head as in the previous em bodiment. In addition, a slight clearance is provided between each nozzle stem 252 and the corresponding ret ainer bore 254 so that the nozzles can shift laterally relative to one another to thereby compensate for tolerance variations in the radial location of the lubricant fittings in a particular pattern thereof.

Since multiple nozzle head 242'can rotate relative to piston rod 250', it can automatically compensate for differences-in the radial location of the entire fitting pattern relative to another fitting pattern. For example, in the illustrated embodiment the head is free to rotate to compensate for a radiallocation variation of plus or minus thirty degrees. The spring loading. of each injection nozzle also compensates for variations in the length of the lubricant fittings relative to one another while the telescopic head compensates for sidesway variations of the conveyor as in the previous embodiment.

When the multiple nozzle head 242 reaches the perpendicular injection position shown in solid lines in FIG. 10 a separate metered charge of lubricant is fed simultaneously to each nozzle via the three lines 260 which of-the conveyor is utilized to pivot the actuator rod 138 to thereby sense the approach of the lubricant fitting patterns of axles 310 and 312. Hence, actuator rod 138 will remain in the raised, engaged position of FIG. 14

, until the outside link 324 has passed out from under rod 133; in other words, until .after the trailing axle 312 has passed the lubricating head 316. Therefore sequence valve 319 is provided to cause retraction of the pair of a lubricating heads, the sequence valve maintaining line 317 closed for a predetermined time interval corresponding to the time required for the .outside link 324 of the conveyor to pass out from under actuating rod 13.8.

When actuating rod 138 returns to the vertical position,

are respectively connected to three lubricant metering valves 172, one for eachnozzle. Simultaneous actuation of-metering valves 172 is obtained by connecting each air line 168 thereof to the outlet of air valve 126.

When it is desired to lubricate a conveyor of the type where successive axle shafts have reversed lubricant fitting pa-tterns, a dual unit lubricating system may be employed utilizing the above described multiple nozzle lubricating heads. Such a dual head setup is shown in FIGS. 14 and 15 for lubricating a conveyor in which the lubricant fitting pattern on axle 310 is reversed relative to the lubricant fitting pattern of the successive axle 312. Two lubricating heads 314 and 3 16 of the above described multiple nozzle type are mounted alongside one another in positions corresponding to the spacing between axles 310zand31 2. The nozzle head 242 of lubricating head 314 is oriented as shown in FIGS. 12 and 13, while the corresponding nozzle head of lubricating head 316 .is turned 180 degrees to correspond to the reversed fitting pattern .ofaxle 310.- This may be easily accomplished without disassembling the nozzle head or piston merely by rotating the nozzle head 180 degrees until the cam rollers 298 again seat in the notches of cam face 296. A slightly modified actuating-system is required for the dual unit setup. Thus, six metering valves 172 are required all of which are simultaneously actuated by connecting line 154 from air valve 148 to an inlet line 317 and an actuating line 318 of a conventional sequence air valve 319. Sequence valve 319 is normally open so as to connect inlet line 317 with a pair of branch lines 320 and 322 respectively connected to the cylinders 52 of heads 314 and 316 to thereby cause the two heads to simultaneously telescope out into engagement with the associated conveyor wheel lubricant fittings. The cycle is the same as previously disclosed except that upon expiration of a predetermined time interval following the opening of air valve 148 and after the injection of lubricant into the fittings has been completed, sequence valve 319 closes inlet line 317-and opens lines 320, 322 to an exhaust portof the sequence valve so that the cylinders are exhausted and can' then retract and I swivel .to .the .ready pick-up position. This addition control valve is necessary since one of theoutside links 324 plunger cam valve 148.is released and sequence valve 319' isexhausted via lines 318 and 154 so that the controls are reset for the next cycle. As in the previous embodiment, the return of the lubricating heads to the ready position causes cams 106 to actuate valves 126 so that the two air inlet lines 164 are closed'and the six air supply lines 168 are opened tothe exhaust port of valves 126, thereby allowing the six lubricant metering valves 172 to be reloaded with a metered charge of lubricant from the high pressure lubricant supply line 174.

We claim:

1. Lubricating apparatus forvlubricating a conveyor having a plurality of lubricant fittings arranged in a pattern on an axle thereof, including in combination a lubricating head adapted to swivel about an axis, a nozzle I retainer mounted on said head and having a plurality of nozzles mounted thereon each having a camming face shaped to center the nozzle on one of said fittings upon engagement of said camming face therewith, said nozzles being mounted on said retainer in a pre-arranged pattern corresponding to the pattern of the lubricant fittings on the axle of the conveyor, said nozzles being independently movablerelative to said retainer in a direction transverse to said axis and parallel to one another, and means for biasing each of saidnozzles individually into engagement with the corresponding-lubricant fitting.

2. Apparatus for lubricating a conveyor moving along a predetermined pathand provided with a lubricant fit- :ting, said apparatus comprising asupport mounted adjacent the path of travel of the conveyor, a head mounted on said support for swivel movement between a pick-up position wherein the head is aligned with a predetermined point in the path of travel of said lubricant fitting as it approaches said support and an injection position wherein the head axis is perpendicular to said path of travel, nozzle means movably mounted on said head, means for causing movement of said nozzle means into engagement with a lubricant fitting on the conveyor in response to said fitting reaching said predetermined point in its travel, the movement of said fitting with the conveyor after engagement by said nozzle means causing said head to swivel to the injection position thereof, meansresponsive to swivel movement of said-headto said injection position for'feeding a charge of'lubricant via said nozzle. means into said fitting andmeans for. retracting said nozzle means and swiveling said head in a reverse direction to the pick-up position thereof, said lubricant feeding means comprising a source, of pressurized lubricant, a lubricant receiving chamber connected at oneend thereof to said source, a differential piston mounted for reciprocal movement in said chamber between said one end thereof and an opposite end of said chamber, the

:tion position thereof for closing said first passage and opening said second passage so that lubricant under pressure from saidsource drives said piston towards the opposite end of said chamber to thereby force the lubricant ahead of said piston via said second passage and said nozzle into the lubricant fitting.

3. Lubricating apparatus as called for in claim 2 including an adjustable stop for limiting travel of said piston towards said one end of said chamber for varying the quantity of lubricant injected into the fitting.

4. Lubricating apparatus for lubricating a conveyor having a plurality of lubricant fittings arranged in a pattern on an axle thereof, including in combination a lubricating head adapted to swivel about an axis, a nozzle retainer mounted on said head and having a plurality of nozzles mounted thereon each having a camming face shaped to center the nozzle on one of said fittings upon engagement of said camming face therewith, said nozzles being mounted on said retainer in a pro-arranged pattern corresponding to the pattern of the lubricant fittings on the axle of the conveyor, said nozzles being independently movable relative to said retainer, and means for biasing each of said nozzles individually into engagement with the corresponding lubricant fitting, said retainer being rotatably mounted on said head for rotation about an axis perpendicular to the swivel axis of the head, and including angular centering means for yieldably urging said retainer to a predetermined angular position relative to said head wherein the nozzle pattern corresponds to the normal position of the lubricant fitting pattern.

5. The combination set forth in claim 4 wherein said angular centering means comprises first and second shafts mounted in said head co-axially with one another and with said retainer, said second shaft having a bore in one end thereof with said first shaft being received in said bore of said shaft, said second shaft having an end surface overlapping said first shaft and being V-shaped to provide a camming surface, said first shaft having a follower roller journalled thereon for rolling contact with said camming surface of said second shaft, one of said shafts being connected for rotation with said retainer and the other shaft being fixed against such rotation, and means for biasing the other of said shafts towards said retainer.

References Cited in the file of this patent UNITED STATES PATENTS 1,262,274 Shelor Apr. 9, 1918 2,030,533 Pate Feb. 11, 1936 2,658,585 Klein et al. Nov. 10, 1953 2,684,733 Freiman July 27, 1954 2,990,916 Hillard et al. July 4, 1961 3,073,415 Dutton et al. Jan. 15, 1963 FOREIGN PATENTS 571,844 Great Britain Sept. 11, 1945 833,819 Great Britain Apr. 27, 1960 

1. LUBRICATING APPARATUS FOR LUBRICATING A CONVEYOR HAVING A PLURALITY OF LUBRICANT FITTINGS ARRANGED IN A PATTERN ON AXLE THEREOF, INCLUDING IN COMBINATION A LUBRICATING HEAD ADAPTED TO SWIVEL ABOUT AN AXIS, A NOZZLE RETAINER MOUNTED ON SAID HEAD AND HAVING A PLURALITY OF NOZZLES MOUNTED THEREON EACH HAVING A CAMMING FACE SHAPED TO CENTER THE NOZZLE ON ONE OF SAID FITTINGS UPON ENGAGEMENT OF SAID CAMMING FACE THEREWITH, SAID NOZZLES BEING MOUNTED ON SAID RETAINER IN A PRE-ARRANGED PATTERN CORRESPONDING TO THE PATTERN OF THE LUBRICANT FITTINGS ON THE AXLE OF THE CONVEYOR, SAID NOZZLES BEING INDEPENDENTLY MOVABLE RELATIVE TO SAID RETAINER IN A DIRECTION TRANSVERSE TO SAID AXIS AND PARALLEL TO ONE ANOTHER, AND MEANS FOR BIASING EACH OF SAID NOZZLES INDIVIDUALLY INTO ENGAGEMENT WITH THE CORRESPONDING LUBRICANT FITTING. 